JP2016166669A - Disc brake device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a disc brake device of a negative type, which is equipped with means for releasing pressing force other than hydraulic pressure, and can improve durability.SOLUTION: In a disc brake device, a piston 28 disposed in a cylinder 20 formed on a caliper body 12 presses a piston side pad 50 by receiving pressing force from an operation spring. The disc brake device is equipped with a supporting portion 22 provided on a part of the caliper body 12; a reaction receiver 34 projecting out to a side part of the piston 28, and opposing to the supporting portion 22; and a cam portion 44 provided between the supporting portion 22 and the reaction receiver 34, and expanding a distance between the supporting portion 22 and the reaction receiver 34 to release the pressing force, by the input of rotation force.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a disc brake device, and more particularly to a disc brake device of a type that generates a braking force during non-operation, which is called a negative type.

  When a disc brake device is used to hold a rotating body in an industrial machine, etc., a negative type disc brake device that uses the disc spring load directly as a braking force generally uses hydraulic force to release the braking force. Known. However, as a whole system of the negative type disc brake device, there is a situation that it is desired to eliminate the space and piping for adopting the hydraulic mechanism and to simplify the size.

  Here, in the disc brake device, as a method for applying a force to the piston by means other than hydraulic pressure, a technique using a cam as disclosed in Patent Document 2 and Patent Document 3 is known. In the disc brake device disclosed in Patent Document 2, an eccentric cam shaft is disposed in a through hole provided in a side surface of the piston, and the eccentric cam shaft is rotated to apply a pressing force to the piston. It has been. Further, the disc brake device disclosed in Patent Document 3 employs a configuration in which a cam lever is disposed at the rear end of the piston and the piston is pushed out to apply a pressing force by rotating the cam lever.

Japanese Utility Model Publication No. 52-113187 JP 2011-271132 A Japanese National Patent Publication No. 10-507811

  Employing a cam mechanism as a braking force release mechanism in a negative type disc brake device is considered to be a very effective means. However, as in the technique disclosed in Patent Document 2, when a configuration in which an eccentric camshaft is arranged in a through hole provided so as to intersect the axial direction of the piston is employed in a negative type disc brake device, When the brake is released, the eccentric camshaft is in a state where a spring force in the direction of bending the shaft is applied. For this reason, in order to ensure safety, there is a problem that the strength of the eccentric camshaft needs to be increased more than necessary, that is, it needs to be thickened.

  Moreover, when it is set as the structure which arrange | positions a cam lever at the rear end of a piston like the technique currently disclosed by patent document 3, the cam lever shall take the structure which pushes back a piston by pressing the front end surface of a piston. Become. However, since the brake pad is arranged on the tip surface of the piston, the configuration disclosed in Patent Document 3 cannot be employed in practice.

  SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a disc brake device that solves the above-described problem and is a negative type disc brake device that includes pressing force releasing means other than hydraulic pressure and that can improve durability. And

  In order to achieve the above object, a disc brake device of the present invention is a disc brake device in which a piston disposed in a cylinder formed in a caliper body presses a brake pad by receiving a pressing force from an operating spring. A support portion provided in a part of the caliper body, a reaction force receiver that protrudes from a side portion of the piston and that faces the support portion, and is provided between the support portion and the reaction force receiver, And a cam portion for releasing the pressing force by increasing a distance between the support portion and the reaction force receiver by input of rotational force.

  In the disc brake device having the above characteristics, the actuating spring is a disc spring arranged in a stacked manner, and a through hole provided in the center of the disc spring slides in the axial direction of the rotor with respect to the caliper body. It is preferable that a holding shaft supported at both ends is arranged so as to be movable.

  With such a feature, there is no possibility that the disc springs arranged in a stacked manner will be displaced, and the position of the piston or the like can be adjusted by the holding shaft.

  Further, in the disc brake device having the above characteristics, the cam portions are arranged so as to form a pair symmetrically with respect to the piston as a base point, and the cam portions forming the pair are paired across the piston. It is preferable that a rotational power input unit connected to the cam unit is connected.

  According to having such a characteristic, the force at the time of canceling the pressing force by the operating spring can be applied with a good balance. Furthermore, by providing a rotational power input unit, it is possible to input the rotational power to both cam portions that form a pair in one operation.

  In the disc brake device having the above characteristics, an actuator for inputting an operating force to the rotational power input unit may be provided on a side surface of the caliper body that faces the position where the operating spring is disposed.

  With such a feature, the disc brake device can be slimmed. Therefore, the free movement of the installation position of the disc brake device can be improved.

  Further, in the disc brake device having the above characteristics, the turning input portion of the cam portion and the actuator may be connected by a connecting member that is inserted through a hole provided in the caliper body.

  By having such a feature, the movable part is not exposed to the outside. Thus, there is no risk of malfunction due to dust adhesion or the like.

In the disc brake device having the above characteristics, the actuator may be an air chamber that operates the connecting member with the force of air.
With such a feature, it is possible to simplify the configuration of the actuator that operates the rotational input portion of the cam portion. Further, since the connecting member is operated by the operation of the air chamber, the responsiveness is good.

  In the disc brake device having the above characteristics, the actuator may be a motor gear unit that applies an operating force in a direction to release the pressing force to the rotational power input portion via the connecting member.

  With such a feature, piping around the actuator can be eliminated. Further, it is possible to eliminate a tank or a compressor that stores a fluid for operating the actuator.

  Further, in the disc brake device having the above characteristics, the motor gear unit is accompanied by a ball screw that rotates by the operation of the motor gear unit, and a ball nut that moves along the ball screw. It can be set as the structure by which a connection member is extruded.

  By having such a feature, even if the generated torque of the motor gear unit is small, the pressing force of the operating spring can be released.

  In the disc brake device having the above characteristics, the connecting member may be provided with a magnetic body, and an electromagnet capable of attracting the magnetic body may be provided at the pushing position of the connecting member.

  By having such a feature, even when the supply of electric power to the motor is interrupted, the state in which the pressing force of the operating spring is released can be maintained.

  Further, in the disc brake device having the above-described characteristics, the holding shaft has a threaded portion between the piston and one of the end portions slides on the caliper body via the piston. It is good to set it as the structure which can adjust a clearance gap with the said brake pad via the said screw part while moving.

  By having such a feature, even when the brake pad is worn and the gap between the rotor and the pad becomes large, adjustment can be made so that the sliding range of the piston becomes an appropriate position. it can.

  Further, in the disc brake device having the above-described characteristics, a flat surface formed along the protruding direction is provided on a side portion of the piston, and the support portion has a surface that contacts the flat surface. Good.

  According to having such a characteristic, a support part will play a role as a rotation stop of a piston.

  According to the disc brake device having the above characteristics, it is a negative type disc brake device, and the pressing force by the operating spring can be released by a mechanism other than hydraulic pressure. Further, it is possible to improve the durability when the cam mechanism is adopted as compared with the conventional cam mechanism.

It is a figure showing the front composition of the disc brake device concerning a 1st embodiment. It is a figure which shows the structure of the right side surface of the disc brake apparatus which concerns on 1st Embodiment. It is a fragmentary sectional view which shows the AA arrow in FIG. It is a fragmentary sectional view which shows the BB arrow in FIG. It is the elements on larger scale for explaining a cam mechanism. It is a disassembled perspective view which shows the structure of the disc brake apparatus which concerns on 1st Embodiment. It is a fragmentary sectional view showing the composition of the disc brake device concerning a 2nd embodiment. It is a partial disassembled perspective view which shows the structure of the disc brake apparatus which concerns on 2nd Embodiment. It is a perspective view which shows the structure of the disc brake apparatus which concerns on 3rd Embodiment. It is sectional drawing which shows the structure of the ABCD cross section in FIG. FIG. 10 is a cross-sectional view showing a state in which a brake is operating in the configuration of the EFGH cross section in FIG. 9. FIG. 10 is a cross-sectional view showing a state in which a brake is released in the configuration of the EFGH cross section in FIG. 9. FIG. 10 is a cross-sectional view showing a state where only the ball nut and the nut holder are pulled back in the configuration of the EFGH cross section in FIG. 9.

  Hereinafter, embodiments of the disc brake device of the present invention will be described in detail with reference to the drawings. In addition, in drawing, FIG. 1 is a figure which shows the front structure of the disc brake apparatus which concerns on 1st Embodiment. FIG. 2 is a diagram showing the configuration of the right side surface in FIG. FIG. 3 is a partial cross-sectional view showing the AA arrow in FIG. FIG. 4 is a partial cross-sectional view showing the arrow BB in FIG. FIG. 5 is a partially enlarged view for explaining the cam mechanism. FIG. 6 is an exploded perspective view showing the configuration of the disc brake device according to the first embodiment.

  The disc brake device 10 according to the first embodiment is configured on the basis of having a caliper body 12, two brake pads (piston side pad 50, claw side pad 56), and an air chamber 62 in appearance. It is supported by a fixed part (not shown) via 66.

  The caliper body 12 basically has a body main body 14, a claw portion 18, and a bridge portion 16. The body main body 14 is provided with a cylinder 20 and a support portion 22, and a case 24 is provided on a side surface opposite to the surface facing the rotor 70, thereby forming a bore 26 as an internal space. The cylinder 20 is provided with a sliding portion 30 of a piston 28 which will be described in detail later. The bore 26 is provided with an operating spring 36, a cam mechanism 42, and the like.

  The piston 28 according to the embodiment includes a sliding part 30 and an interlocking part 32, and a reaction force receiver 34 projects from the outer periphery of the interlocking part 32. The reaction force receiver 34 is a portion to which a reaction force for releasing the pressing force by the operating spring 36 is applied, and is disposed at a position facing the support portion 22 provided in the body main body 14. In such an arrangement configuration, it is possible to release the pressing force by the operating spring 36 by pressing the reaction force receiver 34 with the support portion 22 as a base point. Moreover, the flat part 32a formed along the protrusion direction is provided in the side part of the interlocking | linkage part 32 (refer FIG. 6). The cam portion 44b, which will be described later in detail, is brought into contact with the flat surface 32a, thereby serving as a detent for the piston 28.

  A through hole 30a provided with an internal thread is formed on the inner peripheral side of the sliding portion 30, and an adjustment pin 38 is screwed into the internal thread of the through hole 30a. The adjustment pin 38 plays a role of adjusting the clearance when the piston side pad 50 and the claw side pad 56 that are brake pads are worn, and adjusting the piston 28 to be positioned in an appropriate operating range, and an operation described later. It also serves as a holding shaft for laminating and holding the disc spring as the spring 36. One end of the adjustment pin 38 abuts on the piston-side pad 50, and the other end is configured to protrude to the outside of the case 24. Therefore, the adjustment pin 38 is disposed so as to penetrate both the sliding portion 30 and the interlocking portion 32 of the piston 28 in the axial direction of the piston 28. Therefore, both ends of the adjustment pin 38 are supported by the caliper body 12 via the piston 28 so as to be slidable in the axial direction of the rotor 70.

  The operating spring 36 is a pressing means for pressing the piston 28. In the present embodiment, a plurality of disc springs that are inserted through the other end of the adjustment pin 38 that is screwed into the piston 28 are stacked. The operating spring 36 is disposed between the sliding portion 30 of the piston 28 and the inner peripheral surface of the case 24 constituting the bore 26. The pressing force of the operating spring 36 is adjusted by an adjustment bolt 40 that is screwed into the end of the case 24 after the case 24 is fixed to the body main body 14. The adjustment bolt 40 has a tip projecting into the case 24 and tightens the bolt head to press the operating spring 36 to amplify the repulsive force (pad pressing force) of the operating spring 36.

  The cam mechanism 42 is an element responsible for pushing back the reaction force receiver 34 with the support portion 22 as a base point between the support portion 22 in the body main body 14 of the caliper body 12 and the reaction force receiver 34 in the interlocking portion 32 of the piston 28. It is. The cam mechanism 42 of the present embodiment is basically composed of a cam portion 44 and a lever portion 46. The cam portion 44 is provided so as to correspond to each of the two reaction force receivers 34 provided as a pair via the piston 28.

  The cam portion 44 according to the embodiment includes a cam outer peripheral portion 44b serving as a rotation center and a cylindrical pin 44a disposed on the inner peripheral side of the cam outer peripheral portion 44b. The pin 44a has a length that matches the width of the cam outer peripheral portion 44b. The cam outer peripheral portion 44b includes an arc surface centered on the pin 44a as a sliding surface with the instruction portion 22. And since the cam outer peripheral part 44b is varying the thickness along a circular arc surface, the distance from a pin center to a circular arc surface is changing continuously. The relationship r1 <r2 <r3 is established between r1 to r3 indicating the distance from the center point O shown in FIG.

  By setting it as such a structure, the distance between both can be changed by moving so that the thickness of the cam outer peripheral part 44b located between the support part 22 and the reaction force receiver 34 may be changed. That is, when a portion on the r1 side where the cam outer peripheral portion 44b is thin is disposed between the support portion 22 and the reaction force receiver 34, the piston spring 50, which will be described in detail later, has an operating spring 36. The pressing force due to will work. On the other hand, when a portion on the r3 side where the cam outer peripheral portion 44b is thick is disposed between the support portion 22 and the reaction force receiver 34, the pressing by the operating spring 36 that has acted on the piston-side pad 50 is performed. The pressure will be released. In the assembled state, the cam portion 44 according to the embodiment reduces the thickness of the portion located on the radially outer peripheral side of the rotor 70 and increases the thickness of the portion positioned on the radially inner peripheral side of the rotor 70. Thus, it is set as the structure which changes thickness continuously.

  In the present embodiment, the width d between the contact point P1 of the cam portion 44 with the support portion 22 and the contact point P2 with the reaction force receiver 34 is configured to be smaller than the diameter of the pin 44a. ing. This is to efficiently transmit force.

  A lever portion 46 that connects the two cam outer peripheral portions 44b across the piston 28 is connected to a portion of the cam outer peripheral portion 44b that is thin (a portion that is located on the outer peripheral side in the radial direction of the rotor 70). The lever portion 46 serves as a rotational power input portion that rotates the eccentric member 44b by being tilted in the axial direction of the rotor 70. In the present embodiment, the cam outer peripheral portion 44b can be rotated in a direction in which the pressing force by the operating spring 36 is released by tilting the lever portion 46 to walk away from the rotor 70.

  In the present embodiment, the sliding member 48 is disposed between the support portion 22 and the cam outer peripheral portion 44b, and the eccentric member 44b and the pin 44a, respectively, so as to reduce resistance during sliding. The sliding member 48 may be a roller bearing with a roller or an oilless bearing, and is not particularly limited.

  A piston-side pad 50 is disposed on the surface of the body main body 14 that faces the rotor 70. The piston-side pad 50 is configured on the basis of a lining 52 that is a friction member and a pressure plate 54 made of a steel plate, and the adjustment pin 38 is in contact with the pressure plate 54.

  The claw portion 18 is disposed to face the body main body 14, receives a pressing force via the piston 28, and plays a role of sandwiching the rotor 70 between the piston side pad 50 and the claw side pad 56. For this reason, the nail | claw side pad 56 will be arrange | positioned in the surface facing the rotor 70 in the nail | claw part 18. FIG. The claw side pad 56 is configured based on a lining 58 and a pressure plate 60 in the same manner as the piston side pad 50 described above, and the pressure plate 60 is fastened to the claw portion 18.

  In the disc brake device 10 according to the present embodiment, the operating force is input to the lever portion 46 of the cam mechanism 42 on the outer peripheral side of the claw portion 18, that is, on the side surface opposite to the side surface on which the rotor 70 is disposed. An air chamber 62 is arranged as an actuator for this purpose. By providing the air chamber 62 on the outer peripheral portion on the claw portion 18 side, the body main body 14 and the bridge portion 16 can be slimmed. By connecting the rod 64 to the lever portion 46 of the cam mechanism 42, the air chamber 62 can operate the cam mechanism 42 according to the expansion and contraction of the rod 64.

  The bridge portion 16 serves to connect the body body 14 and the claw portion 18 across the rotor 70. The bridge portion 16 in the present embodiment is provided with a through hole 16 a along the axial direction of the rotor 70. The through hole 16 a communicates the outer periphery of the claw portion 18 and the bore 26 formed in the body main body 14, and allows the rod 64 in the air chamber 62 to be inserted.

  With such a configuration, the cam mechanism 42 and the rod 64 which are movable parts are not exposed to the outside. For this reason, there is no possibility of causing a situation in which dust adheres to the movable part and the sliding part and hinders the operation.

  In the disc brake device 10 configured as described above, in the non-operating state, a pressing force is applied to the piston 28 by the action of the operating spring 36. For this reason, the adjustment pin 38 screwed to the piston 28 presses the pressure plate 54 of the piston side pad 50, and the lining 58 of the piston side pad 50 is pressed against the sliding surface of the rotor 70.

  When the lining 58 of the piston-side pad 50 is pressed against the sliding surface of the rotor 70, the body body 14 in the caliper body 12 slides in a direction away from the rotor 70 due to a reaction force against the pressing. At this time, the claw portion 18 slides in the direction approaching the rotor 70 because it is connected to the body main body 14 by the bridge portion 16 straddling the rotor 70.

  For this reason, the lining 58 of the claw-side pad 56 disposed on the surface of the claw portion 18 facing the rotor 70 is pressed against the sliding surface of the rotor 70. By such an action, the rotor 70 is sandwiched between the piston-side pad 50 and the claw-side pad 56, and maintains a state where the braking force is applied.

  Next, when the air chamber 62 which is an actuator is operated, the rod 64 protrudes toward the body main body 14 side. As the rod 64 protrudes, the lever portion 46 of the cam mechanism 42 tilts in the direction of arrow a (see FIG. 3). When the lever portion 46 is tilted, the eccentric member rotates in the direction of the arrow b (see FIG. 3) with the center O of the pin 44a as a base point, and the reaction force receiver 34 is moved to the arrow c (see FIG. 3) by the change in the thickness. Push back in the direction of. As the reaction force receiver 34 is pushed back, the piston 28 slides in a direction to release the pressing force of the operating spring 36. Thereby, the pressing of the piston side pad 50 and the pressing of the claw side pad 56 which have been pressed by the adjustment pin 38 are released.

  According to the disc brake device 10 according to the present embodiment, the pressing force of the operating spring 36 can be released by using the cam mechanism 42 without using hydraulic pressure. Further, the cam mechanism 42 receives the pressing force of the operating spring 36 in the thickness direction of the eccentric member 44b. For this reason, the durability of the cam mechanism 42 can be improved as compared with the case where the pressing force is applied to the side surface of the rotating shaft as in the cam mechanism disclosed in the prior art.

  Next, a second embodiment of the disc brake device of the present invention will be described with reference to FIGS. Most of the configuration of the disc brake device 10A according to the present embodiment is the same as that of the disc brake device 10 according to the first embodiment described above. Therefore, portions having the same configuration are denoted by the same reference numerals in the drawings, and detailed description thereof is omitted.

  In the disc brake device 10A according to the present embodiment, the arrangement form of the cam mechanism 42 is different from that of the first embodiment. Specifically, in the disc brake device 10 according to the first embodiment, the arc of the eccentric member 44b is disposed toward the body main body 14 and the pin 44a is brought into contact with the reaction force receiver 34. On the other hand, in the disc brake device 10A according to the present embodiment, the arc of the eccentric member 44b is arranged toward the reaction force receiver 34, and the pin 44a is brought into contact with the support portion 22.

  When the cam mechanism 42 has such an arrangement, the action of the cam portion 44 when the lever portion 46 is tilted is reversed. For this reason, the cam portion 44 of the present embodiment is configured to increase the thickness of the portion located on the radially outer peripheral side of the rotor 70 and reduce the thickness of the portion positioned on the radially inner peripheral side of the rotor 70. ing. And the lever part 46 is connected to the site | part with thick thickness.

  In addition, with the difference in the arrangement form of the eccentric member 44b and the pin 44a, the form of the contact surfaces of the support portion 22 and the reaction force receiver 34 is also different. This is for stabilizing the arrangement of the cam outer peripheral portion 44b and the pin 44a. Moreover, in this embodiment, the support part 22 is comprised so that it may become a body main body 14 and a different body. And the support part 22 arrange | positioned at the body main body 14 is set as the structure contact | abutted with respect to the flat surface 32a formed in the side part of the interlocking | linkage part 32 in the piston 28 along the protrusion direction. For this reason, the support portion 22 plays a role as a detent for the piston 28.

  Even when the configuration of the cam mechanism 42 is as described above, the same effect as that of the disc brake device 10 according to the first embodiment can be obtained. In addition, about another structure effect | action and effect, it is the same as that of the disc brake apparatus 10 which concerns on 1st Embodiment mentioned above.

  Next, a third embodiment of the disc brake device of the present invention will be described with reference to FIGS. 9 is a perspective view showing the configuration of the disc brake device according to the embodiment, and FIG. 10 is a diagram showing the configuration of the ABCD cross section in FIG. 11 to 13 are diagrams showing the configuration of the EFGH cross section in FIG.

  Most of the configuration of the disc brake device 10B according to the present embodiment is the same as the disc brake devices 10 and 10A according to the first and second embodiments described above. Therefore, portions having the same configuration are denoted by the same reference numerals in the drawings, and detailed description thereof is omitted.

  In the disc brake device 10B according to the present embodiment, the configuration of the actuator is different from that of the disc brake devices 10 and 10A according to the first and second embodiments described above. Specifically, in the disc brake device 10B according to the present embodiment, the actuator is a motor gear unit 80, and a ball screw unit 90 is attached to the motor gear unit 80, whereby the lever portion 46 constituting the cam mechanism 42 and The rod 64 which is the connecting member is pushed and pulled.

  The motor gear unit 80 includes a motor 82 and a gear unit 84 for transmitting the rotational force of the motor 82 to a ball screw 92 described later. The gear unit 84 is composed of a plurality of gears arranged in the casing 86, and generates torque for rotating the ball screw 92 by changing the gear ratio.

  The ball screw unit 90 is configured based on a ball screw 92, a ball nut 94, an electromagnet 96, an electromagnet plate 98, and a casing 100. The ball screw 92 is a rotating shaft to which the rotational force of the motor 82 is transmitted from the motor gear unit 80 described above. The ball nut 94 is a slider that moves on the ball screw 92 along the axial direction of the ball screw 92 when the ball screw 92 rotates. By adopting such a mechanism, even if the torque generated by the motor 82 and the gear unit 84 is small, the ball screw 92 can be rotated and the pressing force of the operating spring 36 can be released. Become.

  A nut holder 94a is attached to the ball nut 94 according to the embodiment. The nut holder 94a moves along with the operation of the ball nut 94 and plays a role of pressing the electromagnet plate 98 and receiving a pressing force of a preset spring 94b disposed between the casing 100 and the nut holder 94a. When the ball nut 94 is moved to the side where the motor gear unit 80 is arranged, the preset spring 94b pushes back the nut holder 94a by turning off the power supply to the motor 82, and brings the ball nut 94 to the initial position. Play the role of regressing.

  The electromagnet 96 is provided on the side where the caliper body 12 is disposed in the ball screw unit 90 and plays a role of attracting the electromagnet plate 98. The electromagnet plate 98 may be a flat plate made of a magnetic material that is attracted by the operation of the electromagnet 96. The electromagnet plate 98 is a plate to which the rod 64 is fastened, and the rod 64 is pushed out or pulled back when the electromagnet plate 98 moves in the axial direction of the ball screw 92. A guide stud 100 a is disposed between the electromagnet 96 and the casing 100 so as to penetrate the nut holder 94 a and the electromagnet plate 98. In addition, when arrange | positioning the preset spring 94b mentioned above between the nut holder 94a and the casing 100, it is good to arrange | position so that the guide stud 100a may be surrounded.

  The casing 100 is an outer shell that accommodates the above-described ball screw 92, ball nut 94, nut holder 94a, electromagnet 96, electromagnet plate 98, preset spring 94b, and guide stud 100a.

  In the disc brake device 10B having such a configuration, the state in which the nut holder 94a and the electromagnet plate 98 are both positioned at the initial position (motor gear unit 80 arrangement side) as shown in FIG. The pressure is applied, that is, the brake is activated. From such a state, by driving the motor 82 and operating the motor gear unit 80, the ball screw 92 in the ball screw unit 90 is rotated in the normal rotation direction (for example, clockwise rotation). Thereby, the ball nut 94 moves in the arrangement direction of the electromagnet 96 along the axial direction of the ball screw 92. At this time, the nut holder 94 a attached to the ball nut 94 presses the electromagnet plate 98. As a result, the rod 64 is pushed out, the cam mechanism 42 is operated, the release of the pressing force of the operating spring 36 is released, and the brake is released.

  As shown in FIG. 12, when electric power is supplied to the electromagnet 96 when the electromagnet plate 98 is pressed to the electromagnet 96, the electromagnet plate 98 is attracted to the electromagnet 96. Thereby, even if the supply of electric power to the motor 82 is cut off, the brake released state is maintained.

  Here, the ball nut 94 is moved to the holding brake force acting position (initial position) determined by the load of the preset spring 94b and the spring 101 by shutting off the motor power supply.

  After the electromagnet plate 98 is attracted to the electromagnet 96, the motor 82 is supplied with electric power in the opposite phase. As a result, the motor 82 is driven in reverse rotation, and the ball screw 92 that is rotated via the gear unit 84 also rotates in the reverse direction (for example, left rotation). Due to the reverse rotation of the ball screw 92, the ball nut 94 moves together with the nut holder 94a in a direction away from the electromagnet 96. After moving the ball nut 94, the power of the preset spring 94b is received by cutting off the power supply to the motor 82. The ball nut 94 is pushed back to the initial position via the nut holder 94a.

  When the supply of electric power to the electromagnet 96 is interrupted in such a state, the cam mechanism 42 is pushed back by the force of the operating spring 36. Along with this, the rod 64 is also pushed back, and the electromagnet plate 98 to which the end of the rod 64 is fastened comes into contact with the nut holder 94a. In this way, after the electromagnet 96 is attracted and held by the electromagnet 96, the ball nut 94 is pulled back to the initial position, so that when the pressing force of the actuating spring 36 is applied, the motor gear unit 80 becomes the operating resistance. There is no such thing. Therefore, the responsiveness at the time of brake operation can be kept good.

  Even with the disc brake device 10B having such an actuator configuration, the same effects as those of the disc brake devices 10 and 10A according to the first and second embodiments can be obtained.

10, 10A, 10B ......... Disc brake device, 12 ......... Caliper body, 14 ......... Body body, 16 ......... Bridge part, 16a ......... Through hole, 18 ...... Nail part, 20 ... ... Cylinder, 22 ......... Supporting part, 24 ......... Case, 26 ......... Bore, 28 ......... Piston, 30 ......... Sliding part, 30a ......... Through hole, 32 ......... Interlocking part, 32a ......... Flat surface, 34 ......... Reaction force receiving, 36 ......... Operating spring, 38 ......... Adjustment pin, 40 ......... Adjustment bolt, 42 ......... Cam mechanism, 44 ...... Cam part, 44a ......... pin, 44b ......... camera outer peripheral part, 46 ......... lever part, 48 ......... sliding member, 50 ......... piston side pad, 52 ......... lining, 54 ......... pressure plate, 56 ……… Nail pad, 58 ……… Lined, 60 ……… P Pusher plate, 62 ... Air chamber, 64 ... Rod, 66 ... Support, 70 ... Rotor, 80 ... Motor gear unit, 82 ... Motor, 84 ... Gear unit, 86 ... ...... Casing 90 ...... Ball screw unit 92 ...... Ball screw 94 94 Ball nut 94 a Nut holder 94 b Preset spring 96 Electromagnet 98 Electromagnet plate, 100 ... casing, 100a ... guide stud, 101 ... spring.

Claims (11)

A disc brake device in which a piston disposed in a cylinder formed in a caliper body presses a brake pad by receiving a pressing force from an operating spring,
A support provided on a part of the caliper body;
A reaction force receiver that protrudes from a side of the piston and faces the support;
A cam portion that is provided between the support portion and the reaction force receiver and that releases the pressing force by increasing the distance between the support portion and the reaction force receiver by input of rotational force. A disc brake device characterized by that.   The actuating spring is a disc spring arranged in a stacked manner, and both ends are supported in a through hole provided in the center of the disc spring so as to be slidable in the axial direction of the rotor with respect to the caliper body. The disc brake device according to claim 1, wherein a holding shaft is disposed. The cam portions are arranged to form a pair in line symmetry with the piston as a base point,
The disc brake device according to claim 1 or 2, wherein a rotating power input portion connected to the cam portion that is paired across the piston is connected to the cam portion that forms a pair.   The disc brake device according to claim 3, wherein an actuator that inputs an operating force to the rotational power input portion is provided on a side surface of the caliper body that faces the position where the operating spring is disposed.   5. The disc brake device according to claim 4, wherein the rotational power input portion of the cam portion and the actuator are connected by a connecting member that passes through a hole provided in the caliper body.   6. The disc brake device according to claim 5, wherein the actuator is an air chamber that operates the connecting member with the force of air.   The disc brake device according to claim 5, wherein the actuator is a motor gear unit that applies an operating force in a direction to release the pressing force to the rotational force input portion via the connecting member. The motor gear unit is accompanied by a ball screw that rotates by operation of the motor gear unit, and a ball nut that moves along the ball screw.
The disc brake device according to claim 7, wherein the connecting member is pushed out by the ball nut. The connecting member includes a magnetic body,
The disc brake device according to claim 8, wherein an electromagnet capable of attracting the magnetic body is provided at the pushing position of the connecting member.   The holding shaft has a threaded portion between the piston and one of the end portions slides on the caliper body via the piston and the brake pad via the threaded portion. 10. The disc brake device according to claim 2, wherein the clearance is adjustable. 10. A side surface of the piston is provided with a flat surface formed along the protruding direction,
The disc brake device according to claim 1, wherein the support portion has a surface that contacts the flat surface.

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